Hamaker
anti-friction bearings



June 1968 J. D. HAMAKER ANTI-FRICTION BEARINGS 2 Sheets-Sheet 1 OriginalFiled May 27, 196.3

Z w w w m FIG. I

John D Hamoker A'ITORNEYS June 25, 1968 .1. o. HAMAKER 2 Sheets-Sheet 2.

Original Filed May 27 1963 INVENTOR ATTORNEYS United States Patent26,414 ANTI-FRICTION BEARINGS John D. Hamaker, 10126 S. 27th St., OakCreek, Wis. 53154 Original No. 3,194,618, dated July 13, 1965, Ser. No.283,256, May 27, 1963. Application for reissue May 17, 1967, Ser. No.646,749

19 Claims. (Cl. 308-431) Matter enclosed in heavy brackets I: appears inthe original patent but forms no part of this reissue specification;matter printed in italics indicates the additions made by reissue.

This invention relates to new and useful improvements in anti-frictionbearings.

The invention is directed in particular to a bearing of high loadcapacity functioning equivalently to conventional ball bearing in whichthe bearing balls are of quite large radius or diameter, but in whichthe overall dimensions of the bearing are drastically reduced eitherlongitudinally or radially as the occasion may require.

A principal object of the invention is to provide an improvedanti-friction bearing wherein a plurality of bearing members are carriedin a cage member, the bearing members, and consequently, the cagemember, being relatively thin or narrow in one dimension forconservation of space but having convex or spherical end faces receivingthe hearing and struck on a radius of curvature much greater than thetransverse dimensions of the bearing members so as to provide theequivalent static capacity at point of contact of a conventional ballbearing having bearing balls of considerable diameter but without havingthe space requirements of such a bearing.

A further object of the invention is to provide an improvedanti-friction bearing of the character described in the convex bearingfaces have concentric frusto-conical portions for distributing thebearing load over a larger area.

An additional object of the invention is to provide an improvedanti-friction bearing in which the points of support of the bearingloads upon the end faces of the bearing members are restricted toperipheral areas for controlled end wear of the bearing members.

Still another object of the invention is to provide an improvedanti-friction bearing of the character described in which the bearingmembers are arranged in one or more concentric annuli in the cagemember, and may be inclined in any suitable or desirable degree anddirection.

Other and more particular objects will be apparent from a reading of thefollowing description.

A construction designed to carry out the invention will be hereinafterdescribed, together with other features of the invention.

The invention will be more readily understood from a reading of thefollowing specification and by reference to the accompanying drawings,wherein examples of the invention are shown, and wherein:

FIG. 1 is a view, partly in elevation and partly in section,illustrating an anti-friction bearing constructed in accordance withthis invention.

FIG. 2 is a reduced, cross-sectional view taken upon the line 22 of FIG.1,

FIG. 3 is a fragmentary side elevation showing the end portion of one ofthe bearing members,

FIG. 4 is a longitudinal, sectional view of a modified form of theanti-friction bearing,

FIG. 5 is a cross-sectional view taken upon the line 5-5 of FIG. 4,

FIG. 6 is an enlarged, fragmentary, sectional view illustrating amodified form of the end bearing faces of the bearing members,

Re. 26,414 Reisswed June 25, 1968 FIG. 7 is a fragmentary,crosssectional view taken upon the line 77 of FIG. 5, and

FIG. 8 is a view similar to FIG. 7 illustrating an alternate inclinationof the bearing members and an alternate configuration for the endbearing faces thereof.

In the drawings, the numeral 10 designates an annular or agenerally-ring shaped cage member having an upper end face 11, a lowerend face 12 and having an axial bore 13 forming an interior face. Thecage member also has an outer longitudinal face 14 and is formed with aplurality of longitudinal bores or bearing bores 15 opening through theupper face 11 and the lower face 12 and disposed at an oblique anglewith respect to the longitudinal axis of the cage member, in theparticular embodiment shown, the bores 15 being inclined radiallyinwardly at their upper ends toward the bore 13. The bearing bores .15are equidistantly spaced circumferentially of the cage member around theaxial bore 13, and although equidistant spacing is highly desirable, itis not to be considered essential.

Each of the bearing bores 15 receives an elongate hearing member 16,again in the particular embodiment illustrated, the bearings 16 beingcylindrical in configuration, but in any event, the end portions of thebearing members 16 must be circular and the bearing members must berotatable within the bores 15. Each of the bearing members 16 haveconvex or spherical upper and lower bearing end faces 17 having a radiusof curvature much greater than the radius of the bearing members 16themselves, and for optimum performance, the radii of curvature of theend faces 17 should be one-half the over-all length of the bearingmember 16 so that the bearing member, in essence, constitutes acylindrical core taken through the center of a relatively large sphere.The bearing members 16 are rotatable in the bores 15, but are veryclosely fitted thereto so as to have a minimum of lateral clearance andplay or movement.

The bearing members 16 have axial lengths greater than the bearing boresin which they are received and may have lengths greater or less thantwice the radii of curvature of the end faces 17, but as this optimumdimension is varied, greater or lesser lateral forces upon the bearingmembers 16 will come into existence tending to tilt the bearing membersin the bearing bores 15 and resulting in additional friction and wearbetween the bearing members and the bearing bores. The angle ofinclination of the bearing members and the bearing bores may be variedsomewhat, it usually being desirable to maintain the angularity of theorder of magnitude of a few degrees up to 8 or 10' or more, and it ispreferable that the line extending between the contact or bearing pointson the faces 17 intersect the longitudinal center of the bearing members16 at the transverse center thereof and be parallel to the longitudinalaxis of the bearing cage. Thus the axes of thrust transmission betweenthe thrust members and the respective ends of the bearing member aresubstantially coincident. In this way, a true, rolling-actionanti-friction bearing is produced. Of course, the bearing members 16,along with the cage member 10 may be heattreated, hardened, plated, andotherwise conventionally treated as may be found suitable or desirable.

The bearing structure is adaptable not only for use as an axial thrusthearing as illustrated in the drawings to withstand thrusts deliveredaxially along a shaft or other rotating member, but may also be used forwithstanding radial thrusts simply by constructing the cage member 10 ofsuitable radial dimensions and with more or less radially directedbearing bores so as to provide a relatively wide but very fiat bearinghaving a performance equivalent to that of a comparable ball bearingwhich, of course, would have a much larger axial thickness. Further, thebearing members 16 may be inclined inwardly as shown or outwardly, asmay be desired, alternate ones of the bearing members may be inclinedinwardly while the remaining are inclined outwardly, or selected ones ofthe bearing members may be inclined in either direction as may bedesired, it being important that the relative angles of inclination bekept equal and opposite, it also being desirable that the distributionof the inwardly and outwardly inclined bearing members, if sucharrangement is utilized, be symmetrical about the axis of the cagemember 10. In many cases, an alternation or judicious balancing ofinward and outward inclinations may avoid undesirable longitudinalthrusts upon the bearing cage.

The bearing members 16, are, of course, of greater axial length than theaxial lengths of the bearing bores so as to project beyond the end facesthereof, as illus trated, and many different arrangements may beemployed for receiving from or transmitting to the end faces 17 of thebearing members, the thrusts and loads to be withstood. In the form ofthe invention shown in FIG. I, a shaft 18 is formed with an axial pin 19forming a shoulder 20 and a circumferential seating face 21 upon the pin19 adjacent the shoulder 20. The pin 19 is received in a collar 22having an axial seating bore 23 at its upper end adjoined by acounterbore 24 in which the face 21 seats,

and carrying at its lower end an outwardly extending annular flange 24against the lower side of which the shoulder 20 abuts. Desirably, theface 21 has a press fit in the counterbore 24, and the upper end of thepin 19 has a press fit in the seating face or bore 23 so that the collar19 revolves with the shaft 18.

The axial bore 13 of the cage member 10 has a sliding fit over the outersurface of the pin 19, the lower end faces 17 of the bearing members 16engaging the upper surface of the shoulder 24. A second shaft or supportmember 25 carries a cylindrical box 26 with a seating face 27 formed atthe upper end of its interior and adjoined by a downwardly extendingcounterbore 28. A second collar 29 has an external seating face 30 atits lower end for a press fit in the lower end of the box 26, its upperexterior portion being reduced in diameter for a press fit with relationto the seating face 27. An inwardly extending annular flange 31 isprovided at the upper end of the collar 29, its upper surface abuttingthe bottom of the box 26, while its lower surface adjoins the upper endhearing faces 17 of the bearing members 16. Suitable needle or pinbearings 32 and 33 are provided between the upper end of the collar 22and the inner face of the flange 31, and between the lower interior endof the box 26 and the outer face of the flange 24, respectively.

With this arrangement, endwise relative thrusts between the shafts ormembers 18 and 25 are transferred to the flanges 24 and 31, and thenceto the end bearing faces 17 of the bearing members 16. The bearingfaces, having radii of curvature very much greater than the transversedimensions of the members 16, and the members 16 being freely rotatableor revolvable in the bearing bores 15, a true rolling-action functionthe same as achieved by spherical ball bearings having a diameter equalto the axial length of the members 16 is obtained, and the bearingwithstands the same bearing loads without requiring such largetransverse dimensions or radial dimensions as are required byconventional ball bearings. Indeed, the only limit upon the loads towhich the bearing members 16 may be subjected are those loads that themembers are capable of withstanding in columnar stress. In general, themore nearly the inclination of the bearing members 16 approaches thevertical or parallel to the longitudinal axis of the cage member 10, thegreater the loads which may be withstood without excessive heating ofthe bearing; whereas the greater the angularity of the bearing membersand the nearer the point of thrust application approaches theperipheries of the end faces 17, the greater the speeds at which thehearing may be utilized without overheating, this being due to the factthat the more nearly the bearing point approaches the peripheries of theend faces 17, the slower the bearing members 16 revolve within the bores15 in relation to the relative speed of rotation between the members 18and 25. In this thrust application of the anti'friction bearing, thebearing members 16 achieve a true rolling action and there is norelative slippage between the end faces 17 and the flanges 24 and 31. Inthe utilization of the bearing structure for withstanding radialthrusts, however, there will be different speeds of movement of thesurfaces engaging the end faces 17 as between the opposite ends of themembers 16, and accordingly some slippage must necessarily occur.

A modified form of the anti-friction bearing is shown in FIG. 4 of thedrawings and includes an annular or generally ring-like cage member 34having an outer longitudinal face 35 and upper and lower end faces 36and 37, respectively. The cage member also has an axial bore 38 formingan interior face. The cage member is provided with an outer or firstannulus of equidistantly spaced bearing bores 39 which, in theparticular embodiment illustrated, are inclined radially outwardly fromtheir lower ends to their upper ends and open through both the upper andlower faces 36 and 37 of the cage member.

The cage member also is formed with a second or inner annulus of bearingbores 40 equidistantly spaced about the center or axis of the cagemember 34, and also being inclined radially outwardly from their lowerends to their upper ends and projecting through the upper and lower endfaces of the cage member.

Each of the bearing bores 39 and 40 receives an elongate bearing member41, circular in cross-section at its end portions and being freelyrotatable within the bearing bores, it being noted that while thebearing members 41 are freely rotatable within the bearing bores theyare closely fitted thereto as by lapping or grinding so as to have aminimum of side or lateral clearance and hence a minimal degree oflateral movement within the bearing bores, both to reduce wear as wellas to prevent lateral tilting and relative misalining between theseveral bearing members. The bearing members 41 are of such alongitudinal or axial length as to extend through the end faces 36 and37 of the cage member, each end face 42 of each bearing member beingconvex or spherical in configuration so as to provide end load-bearingfaces equivalent to those typical of ball bearings of a diameter equalto twice the radius of curvature of the end faces 42. Again, for optimumresults, the radius of curvature of the end faces 42 should be twice theaxial lengths of the bearing members 41, but greater or lesser axiallengths may be employed with concomitant variation in the mechanicalfunctioning of the bearing members as bearings.

A first shaft or thrust member 43 is formed with an elongate axial pin44, of reduced diameter, having a loose or sliding fit within the axialbore 38 of the cage member 34 and provided with an annular, outwardlyextending shoulder 45 surrounding the base of the pin 44 and receiving acircular washer or bearing disk 46 upon which the lower end faces 42 ofthe bearing members 41 engage. A similar bearing disk or washer 47 isreceived upon the upper end of the pin 44 and has an underside engagingthe upper end faces 42 of the bearing members.

A second thrust member 48, which may or may not be tubular, is formed onits lower end with a depending, hollow, cylindrical box 49, the bottom50 of which engages the upper face of the bearing disk 47, the bottom ofthe box having a reduced axial bore receiving a needle or pin bearing 51encompassing a bearing bushing 52 having a press fit upon the upperextremity of the pin 44. A second needle or pin bearing 53 is receivedbetween the outer periphery of the first thrust member 43 and theinterior of the lower portion of the box 49.

In function, the second form of the invention is in many respectssubstantially the same as that of the first described form. and the sameremarks apply thereto. It is noted that the second modification makesprovision for a greater number of the bearing members 41 within a givencross-sectional space, and it further being apparent that the concentricrows or annuli of the bearing members 41 may be increased or multipliedas may be found suitable or advantageous for the particular bearingproblem at hand.

As previously noted, alternate ones of the bearing members 41 in thefirst or outer annulus may be inclined either inwardly or outwardly,alternatively or any other suitable fashion, and the same applies to theinner row of bearing members which, as shown in FIG. 7 are inclinedradially in the same direction and to the same extent as those of theouter annulus. However, the bearing members in one annulus may beinclined in one direction and those in the other annulus in the oppositedirection, as shown in FIG. 8, wherein the inner bearing members areindicated as being inclined at an angle equal and opposite to that ofthe angle of inclination of the outer bearing members.

Further, the bearing members of any of the modifications of theinvention may be modified as shown in FIG. 8 to provide a constantbearing surfaces. As is true with any bearing, the bearings of thepresent invention will wear through prolonged use, and as such wearoccurs, the relatives areas of the end bearing faces of the bearingmembers will tend to increase in size, thus altering the operatingcharacteristics of the bearing, introducing additional friction factorsand otherwise modifying the performance of the bearing. When it isdesirable to maintain the bearing areas of the end bearing faces of thebearing members substantially uniform throughout the operating or usefullife of the bearing, the bearing members, may, as noted, be modified inaccordance with the modification of FIG. 8 of the drawings in which thecage member 54 is provided with the longitudinal inclined bearing bore55 having rotatably mounted therein a bearing member 56, and beingsuitably disposed in the subject structure as within a surroundingmember or element 57, an upper thrust member 58 and a lower thrustmember 59. The bearing member 56 is elongate and generally cylindricalin configuration, although other configurations may readily be employedso long as the bearing member is rotatable within the bearing bore 55and projects through the upper and lower end faces of the cage member54. The end bearing faces of the bearing member 56 again have thespherical or convex configuration previously described with theexception that a cylindrical, axial, recess 60 is formed centrally ofeach of the b aring faces, extending an appreciable distance axially ofthe bearing member 56 so as to leave exposed of the end bearing facesessentially only a peripheral marginal portion 61 which forms an annularpart of the outermost section or periphery of the end bearing faces, andconstitutes the area of the bearing faces upon which the hearing loadsor thrusts are applied. The walls of the recesses 60 are parallel to theouter walls of the bearing members 56, at least at the end portionsthereof, and accordingly, narrow annuli 62 of constant cross-section areformed between the side walls of the recesses 60 and the outer walls ofthe bearing member 56. Thus, as the bearing faces 61 wear down, theyremain constant in exposed area, providing a presumably constant rate ofwear, but more importantly presenting a constant bearing area regardlessof the degree of wear which may have occurred.

It is highly desirable to supplement this structure by providing uponthe thrust members 58 and 59 annular bearing ribs 63 upon which thebearing faces 61 ride and which are also of a substantially constantcross-sectional area viewed in axial cross-section so that as the ribs63 wear away, there will continue to be ex osed a more or less constantbearin area for the bearing faces 61, and more importantly, there willbe no requirement that the bearing faces 61 cut an ever larger groove inthe thrust members 58 and 59 which would tend to increase the frictionaland bearing load applied due to the wearing of the thrust elements ormembers 58 and 59 over larger or wider areas as the bearing areas 61move thereinto.

It is also to be noted that the bearing member 56 of the modification ofFIG. 8 is shown as inclined at an equal but opposite angle to thebearing member 41 of FIG. 7, illustrating the modification of tiltingthe bearing members either in one direction or the other as may bedesired.

Yet another modification applicable to all forms of the invention isshown in FIG. 6 in which the spherical or convex end bearing faces 64 ofthe bearing members 65 are modified by having formed thereon afrusto-conical section 66 having its margins spaced from the peripheryof the bearing member 65 as well as the central axis thereof, but beingconcentrically positioned with respect to the longitudinal axis of thebearing member 65, the latter, of course, being carried in the usualcage member 67, and the bearing member engaging a suitable thrust member68.

This modification makes provision for increased areas of application ofthe bearing loads on the bearing end faces of the bearing members inthat the load may be applied entirely across a radial line on thefrusto-conical area 65 and areas adjacent thereto rather than thetheoretical application of the bearing load to a single point and theimmediately surrounding area as is the case with truly spherical ballbearings and the bearing members of this invention having spherical orconvex end faces. It is noted, however, as set forth herein and as usedin this description and the claims appended hereto, the words generallyconvex" apply not only to end bearing faces representing sections oftrue spherical faces, but also, such faces modified with thefrusto-conical section, as illustrated in the form of the inventionshown in FIG. 6, as well as the form of the invention shown in FIG. 8 inwhich the convex or generally convex faces of the bearing members aremodified by the shallow axial bores 60. The modification of FIG. 6 willwithstand greater bearing loads than those of the other modifications,but it is also noted, that the truly spherical configurations of thepreviously described bearing members may, in the course of time, and asexpected wear occurs, approach the configuration of that of FIG. 6. Inaddition, the thrust members upon which the end bearing faces of thebearing members ride or roll, will tend to develop circular bearingpatterns or grooves conforming to the configuration of the end faces ofthe bearing members, so that the thrust members and the bearing membersmore or less wear into a close conformity and snug fit with respect toone another, and further, that the portions of the faces of the thrustmembers engaged by the end bearing faces of the bearing members mayinitially receive, or be formed with, circular grooves of variousconfigurations to function much in the same manner as the races for aconventional ball bearing function.

Thus, the invention is subject to much modification, both of the endbearing faces of the bearing members and the faces of the thrust memberswhich they engage, the degrees, directions and relative angularity ofdisposition of the several bearing members, the axial lengths of thebearing members, and the like. In all instances, however, theanti-friction bearing of this invention utilizes an elongate bearingmember having generally convex end bearing faces of a radius ofcurvature somewhat greater or much greater than the transversedimensions or transverse diameter of the bearing members, and utilizes aplurality of such bearing members to provide the full operativeequivalent of conventional ball bearings of much greater radial or axialdimensions. Of course, the preferred application of the invention is tohearings in which axial loads are to be withstood, or in which, theprimary function of the elongate bearing members is to withstand thrustloads as contrasted to radial loads. In other words, the invention isprimarily applicable to bearing means for a shaft in which the bearingmeans withstands 7 the endwise thrust of the shaft rather than theradial loads thereof.

The foregoing description of the invention is explanatory thereof andvarious changes in the size, shape and materials, as well as in thedetails of the illustrated construction may be made, within the scope ofthe appended claims, without departing from the spirit of the inventron.

What I claim and desire to secure by Letters Patent is:

1. An anti-friction load-sustaining bearing including a plurality ofelongated roller-shaped bearing members of circular cross-section havingsubstantially spherical hearing load-sustaining end bearing faces oneach end for carrying substantially the entire bearing load, the endfaces having a general radius of curvature of the magnitude of onchalfthe axial length of the bearing members, the bearing members being ofmuch greater length than diameter, a cage member for the bearing membersof generally ring shape having end faces and an axial bore forming aninternal face, the cage member having an outer longitudinal face and aplurality of bearing bores receiving the beating members in rotatablerelationship, the bearing bores being inclined at an oblique angle withrespect to one axis of the cage member and opening through opposed facesof the cage member, the bearing bores having axial lengths less than theaxial lengths of the bearing members.

2. An anti-friction load-sustaining bearing including a plurality ofelongated roller-shaped bearing members of circular cross-section havingconvex bearing load-sustaining end bearing faces on each end forcarrying substantially the entire bearing load, the end faces having ageneral radius of curvature of the magnitude of one half the axiallength of the bearing members, the bearing members being of much greaterlength than diameter, a cage member for the bearing members of generallyring shape having end faces and an axial bore and an outer longitudinalface, the cage members having a plurality of longitudinal boresreceiving the bearing members in rotatable relationship, thelongitudinal bores being radially inclined with respect to thelongitudinal axis of the cage member and opening through the end facesof the cage member, the longitudinal bores having axial lengths lessthan the axial lengths of the bearing members.

3. An anti-friction load-sustaining bearing including a plurality ofelongated roller-shaped bearing members of circular cross-section havingconvex bearing load-sustaining end bearing faces on each end forcarrying substantiah ly the entire bearing load, the end faces having ageneral radius of curvature of the magnitude of one-half the axiallength of the bearing members, the bearing members being of much greaterlength than diameter, a cage memrer for the bearing members of generallyring shape having end faces and an axial bore forming an internal face,the cage member having an outer longitudinal face and a plurality ofbearing bores receiving the bearing members in rotatable relationship,the bearing bores being inclined at an oblique angle with respect to oneaxis of the cage member and opening through opposed faces of the cagemember, the bearing bores having axial lengths less than the axiallengths of the *bearing members, the convex end bearing faces of thebearing members having frustoconical bearing areas disposedconcentrically thereon.

4. An anti-friction load-sustaining bearing including a plurality ofelongated roller-shaped cylinder bearing members of circular crosssection having convex bearing loadsustaining end bearing faces on eachend for carrying substantially the entire bearing load, the end faceshaving a general radius of curvature of the magnitude of one-half theaxial length of the bearing members, the bearing members being of muchgreater length than diameter, a cage member for the bearing members ofgenerally ring shape having end faces and an axial bore and an outerlongitudinal face, the cage member having a plurality of longitudinulbores receiving the beating members in rotatable rclutionship, thelongitudinal bores being inclined with respect ill) to the longitudinalaxis of the cage member and opening through the end faces of the cagemember, the longitudinal bores having axial lengths less than the axiallengths of the bearing members.

5. An anti-friction load-sustaining bearing including a cage member ofgenerally cylindrical shape having end faces and an outer longitudinalface along with an axial bore forming an internal face, the cage memberhaving a plurality of bearing bores surrounding its axial bore withtheir longitudinal axes inclined at an oblique angle with respect to oneaxis of the cage member, the bearing bores being equidistantly spacedcircumferentially of the cage member and extending through opposed facesthereof, and an elongated roller-shaped bearing member of circularcross-section in each of the bearing bores and having convex bearingload-sustaining end bearing faces on each end for carrying substantiallythe entire bearing load, the end faces having a radius of curvature muchgreater than the transverse radius of the bearing members, the bearingmembers having axial lengths greater than the axial lengths of thebearing bores, the bearing members being of much greater length thandiameter.

6. Art anti-friction load-sustaining bearing including an integral cagemember of generally cylindrical shape having end faces and an outerlongitudinal face along with an axial bore forming an internal face, thecage member having a first set of a plurality of bearing boressurrounding its axial bore with their longitudinal axes inclined at anoblique angle With respect to one axis of the cage member, the bearingbores of the first set being equidistantly spaced circumfcrentially ofthe cage member and extending through opposed faces thereof, the cagemember having a second set of a plurality of bearing bores surroundingits axial bore concentrically of the first set with their longitudinalaxes inclined at an oblique angle with respect to one axis of the cagemember, the bearing bores of the second set being equidistantly spacedcircumferentially of the cage member and extending through opposed facesthereof, and an elongated roller-shaped bearing member of the circularcross-section in each of the bearing bores and having convex bearingload-sustaining end bearing faces on each end for carrying substantiallythe entire bearing load, the end faces having a radius of curvature muchgreater than the transverse radius of the bearing members, the bearingmembers having axial lengths greater than the axial lengths of thebearing bores, the bearing members being of much greater length than thediameter.

7. An anti-friction load-sustaining hearing as set forth in claim 6wherein bearing bores of both sets of bores are inclined in the sameradial direction.

8. An anti-friction load-sustaining hearing as set forth in claim 6wherein the bearing bores of each set of bores are inclined in oppositeradial directions.

9. An anti-friction load-sustaining bearing as set forth in claim 5 anda first thrust member encompassing the cage member, the first thrustmember having a face adapted to transfer thrust to one end of thebearing members, and a second thrust member received within the axialbore of the cage member and having a face adapted to transfer thrust tothe other end of the bearing members, one thrust member being rotatablewith respect to the other thrust member.

10. An anti-friction load-sustaining bearing as set forth in claim 5'and a first thrust member having a box encompassing the cage member, thebox having a bottom adapted to transfer thrust to one end of the bearingmembers, and a second thrust member having a pin received Within theaxial bore of the cage member and a shoulder surrounding the pin adaptedto transfer thrust to the other end of the bearing members, one thrustmember being rotatable with respect to the other thrust member, andlateral-thrust friction members between the two thrust members.

ll. An anti-friction load-sustaining hearing as set forth in claim 5wherein the convex end bearing faces of the bearing members havefrusto-conicnl bearing areas disposed concentrically thereon.

12. An anti-friction load-sustaining bearing including an integral cagemember of generally cylindtical shape having end faces and an axial borealong with an outer longitudi nal face, the cage member having a firstset of a plurality of bearing bores surrounding its axial bore withtheir longitudinal axes inclined radially with respect to thelongitudinal axis of the cage member, the bearing bores of the first setbeing equidistantly spaced circumferentially of the cage member andextending through its and faces, the cage member having a second set ofa plurality of bearing bores surrounding its axial bore concentricallyof the first set with their longitudinal axes inclined radially withrespect to the longitudinal axis of the cage member, the bearing boresof the second set being equidistantly spaced circumferentially of thecage member and extending through its end faces, and an elongatedroller-shaped bearing member of circular Cress-section in each of thebearing bores and having convex bearing loadsustaining end bearing faceson each end for carrying substantially the entire bearing load, the endfaces having a radius of curvature much greater than the transverseradius of the bearing members, the bearing members having axial lengthsgreater than the axial lengths of the bearing bores, the bearing membersbeing of much greater length than diameter.

13. An anti-friction loadsustaining bearing as set forth in claim 5wherein the bearing members have axial circular recesses in their endbearing faces.

14. An anti-friction load-sustaining bearing as set forth in claim 5 anda first thrust member encompassing the cage member, the first thrustmember having a face adapted to transfer thrust to one end of thebearing members, and a second thrust member received within the axialbore of the cage member and having a face adapted to transfer thrust tothe other end of the bearing members, one thrust member being rotatablewith respect to the other thrust member, the bearing members havingaxial circular recesses in their end bearing faces, and the thrustmembers having annular bearing ribs engaged by the end bearing faces ofthe bearing members.

15. An anti-friction load-sustaining bearing structure comprising anaxially elongated roller-shaped bearing member and axially spaced thrustmembers at the ends of the bearing member, said bearing member being ofmuch greater length than width, the respective ends of the bearingmember and respective thrust members having facing surfaces inload-transmitting contact, the end surfaces of the bearing member beinggenerally convex, said bearing member having its longitudinal axisinclined at an oblique angle with respect to the surfaces of said thrustmembers whereby the arm of contact between said lacing surfaces at oneend of the bearing member is at one side of said axis and the area ofcontact between said facing A'LlljflCIS at the other end of .roidbcm'ing member is at the other side of said axis, the axes of thrusttransmission be- Iwccn the thrust members and the respective ends 0 thebearing member being substantially coincident whereby the load imposedon one thrust member is directly opposed by the load imposed on theother thrust member along the substantially coincident axes of thrustthrough the bear ing, member.

16. The bearing structure of claim 15 in which there is a cage laterallysupporting said bearing member with its longitudinal axis inclined atsaid oblique angle and within which said bearing member turns on saidlongitudinal axis.

17. The bearing structure of claim IS in which relarive motion of saidthrust members will impose turning torque on said bearing member tocause the convex end surfaces of the bearing member to roll on thefacing surfaces of the thrust members and the bearing member to turn onits longitudinal m'is.

I8. The bearing structure of claim 17 in which there are a plurality ofsuch bearing members between said thrust members, said thrust memberscomprising faces which sweep across the ends of said bcuring members ingenerally opposite directions during such relative motion.

19. The bearing slrucrure of claim 18 in which the relative motion 0]said thrust members rotates said membe rs concentrically.

References Cited The following references, cited by the Examiner, are ofrecord in the patented file of this patent or the original patent.

UNITED STATES PATENTS 2,735,934 3/1957 Alderstam 308-235 X 2,430,35911/1947 Messinger 308-174 X 2,174,325 9/1939 Large 308-235 X 1,840,6071/1932 Scribner 308-218 663,435 12/1900 Heath 308-215 X 525,404 9/1894Carman 308-229 X 352,841 11/1886 Starley 308-217 1,670,433 5/1928 Barks308-217 FOREIGN PATENTS 370,932 1/1907 France.

MARTIN P. SCHNADRON, Prinmry Examiner.

FRANK SUSKO, Examiner.

